CN105671902B - Condensing type clothes dryer and control method thereof - Google Patents

Condensing type clothes dryer and control method thereof Download PDF

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Publication number
CN105671902B
CN105671902B CN201510898057.2A CN201510898057A CN105671902B CN 105671902 B CN105671902 B CN 105671902B CN 201510898057 A CN201510898057 A CN 201510898057A CN 105671902 B CN105671902 B CN 105671902B
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CN
China
Prior art keywords
evaporator
flow path
air
condenser
bypass flow
Prior art date
Application number
CN201510898057.2A
Other languages
Chinese (zh)
Other versions
CN105671902A (en
Inventor
李勇柱
朴大润
柳秉助
Original Assignee
Lg电子株式会社
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Filing date
Publication date
Priority to KR1020140175163A priority Critical patent/KR101632013B1/en
Priority to KR10-2014-0175163 priority
Application filed by Lg电子株式会社 filed Critical Lg电子株式会社
Publication of CN105671902A publication Critical patent/CN105671902A/en
Application granted granted Critical
Publication of CN105671902B publication Critical patent/CN105671902B/en

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    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00Domestic laundry dryers
    • D06F58/20General details of domestic laundry dryers 
    • D06F58/24Condensing arrangements
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00Domestic laundry dryers
    • D06F58/20General details of domestic laundry dryers 
    • D06F58/206Heat pump arrangements
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00Domestic laundry dryers
    • D06F58/02Domestic laundry dryers having dryer drums rotating about a horizontal axis
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00Domestic laundry dryers
    • D06F58/30Drying processes 
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F2103/00Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F2103/00Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
    • D06F2103/02Characteristics of laundry or load
    • D06F2103/08Humidity
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F2103/00Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
    • D06F2103/28Air properties
    • D06F2103/36Flow or velocity
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F2103/00Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
    • D06F2103/50Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers related to heat pumps, e.g. pressure or flow rate
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F2105/00Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
    • D06F2105/16Air properties
    • D06F2105/24Flow or velocity
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F2105/00Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
    • D06F2105/26Heat pumps
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00Domestic laundry dryers
    • D06F58/20General details of domestic laundry dryers 
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00Domestic laundry dryers
    • D06F58/32Control of operations performed in domestic laundry dryers 
    • D06F58/34Control of operations performed in domestic laundry dryers  characterised by the purpose or target of the control
    • D06F58/36Control of operational steps, e.g. for optimisation or improvement of operational steps depending on the condition of the laundry
    • D06F58/38Control of operational steps, e.g. for optimisation or improvement of operational steps depending on the condition of the laundry of drying, e.g. to achieve the target humidity
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B40/00Technologies aiming at improving the efficiency of home appliances, e.g. induction cooking or efficient technologies for refrigerators, freezers or dish washers
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10STECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00Heat exchange
    • Y10S165/913Condensation

Abstract

The invention discloses a condensing clothes dryer and a control method thereof, the condensing clothes dryer of the invention comprises: a drum for accommodating the dried object; a circulation duct for circulating air through the drum; a circulation fan for flowing air; a heat pump cycle including an evaporator and a condenser which are disposed in the circulation duct in a spaced manner, the heat pump cycle absorbing heat of air discharged from the drum and transferring the heat to air flowing into the drum; a bypass flow path formed in the circulation duct, for bypassing a part of air discharged from the drum around the evaporator, and merging the air passing through the evaporator on an upstream side of the condenser; and an opening/closing means for selectively opening/closing the bypass flow path.

Description

Condensing type clothes dryer and control method thereof
Technical Field
The present invention relates to a condensing type laundry dryer for drying laundry using a heat pump and a control method thereof.
Background
In general, a clothes dryer is a device for drying laundry by supplying hot air generated by a heater into a drum and evaporating moisture contained in the laundry.
Laundry dryers may be classified into exhaust type laundry dryers and condensing type laundry dryers according to the manner of processing the humid air passing through the drum after drying the laundry.
The exhaust type clothes dryer is used for exhausting air in a humid state, which passes through a drum and is exhausted, to the outside of the dryer, and the condensing type clothes dryer circulates without exhausting the humid air, which passes through the drum and is exhausted, to the outside of the dryer, and cools the humid air to a temperature below a dew point temperature through a condenser, thereby condensing moisture contained in the humid air.
The condensing type laundry dryer heats the laundry by the heater before supplying the condensed water condensed in the condenser to the drum again, and then allows the heated air to flow into the drum. In which the moist air is cooled in the process of being condensed to cause a loss of heat energy possessed by the air, and an additional heater, etc. are required in order to heat the air to a temperature required for drying.
The exhaust type dryer also needs to exhaust high-temperature humid air to the outside and to flow in normal-temperature outside air, to be heated to a desired temperature level by a heater, etc. In particular, as the drying is performed, the humidity of the air discharged from the outlet of the drum is reduced, which causes drying of the objects not used in the drum, and heat of the air discharged to the outside is damaged, thereby reducing thermal efficiency.
Therefore, recently, a laundry dryer having a heat pump cycle is introduced, which can improve energy efficiency by heating air flowing into a drum along with recovering energy discharged from the drum.
Fig. 1 is a schematic diagram showing an example of a condensing type laundry dryer to which a heat pump cycle is applied.
As explained with reference to fig. 1, the condensing type laundry dryer includes: a drum 1 for putting the object to be dried; a circulation duct 2 providing a flow path for circulating air through the drum 1; a circulation fan 3 for circulating air along the circulation duct 2; the heat pump cycle 4 has an evaporator 5 and a condenser 6 provided in series in the circulation duct 2 so that the air circulating along the circulation duct 2 passes therethrough.
The heat pump cycle 4 may include: a circulation pipe forming a circulation flow path so that a refrigerant circulates via the evaporator 5 and the condenser 6; and a compressor 7, an expansion valve 8, a circulation pipe provided between the evaporator 5 and the condenser 6.
The heat pump cycle 4 configured as described above transfers the thermal energy of the air passing through the drum 1 to the refrigerant through the evaporator 5, and then transfers the thermal energy of the refrigerant to the air flowing into the drum 1 through the condenser 6. Thus, the hot wind can be generated by using the heat energy discarded in the conventional exhaust type clothes dryer or lost in the condensing type clothes dryer.
On the other hand, fig. 2 is a diagram illustrating the flow of air passing through the evaporator 5 and the condenser 6 in the condensing laundry dryer to which the heat pump cycle 4 is applied.
Referring to fig. 2, the air discharged from the drum 1 passes through the evaporator 5 and the condenser 6 in order along the circulation duct 2.
Here, the circulation duct 2 and the evaporator 5 (and the condenser 6 are also the same) are formed by a structure having no gap therebetween, so that the maximum amount of air passes through the evaporator 5 and the condenser 6. The advantage is that the passing wind speed and heat transfer coefficient of the evaporator 5 and the condenser 6 are increased to improve the heat exchange efficiency, thereby reducing the drying time and energy.
However, the structure without a gap between the circulation duct 2 and the heat exchanger (including the evaporator 5 and the condenser 6) has the following problems.
Generally, as drying is performed in the dryer, the outlet temperature of the drum 1 rises, so that the evaporation pressure of the refrigerant evaporated in the evaporator 5 and the condensation pressure of the refrigerant condensed in the condenser 6 rise.
When the amount of the drying load is large or the amount of water contained in the initially dried material is large, the condensing pressure may increase to or above the reliability securing pressure of the compressor 7 as the drying time increases. This causes the condensation temperature of the condenser 6 and the discharge temperature of the compressor 7 to increase, which may cause various problems, and in this case, the condensation temperature of the condenser 6 and the discharge temperature of the compressor 7 are controlled to be equal to or lower than the predetermined temperature.
In order to solve such a phenomenon, the following method is proposed.
For example, the INVERTER COMPRESSOR (INVERTER COMPRESSOR) may change the rotation speed, so that when the condensing pressure of the condenser increases, the rotation speed of the COMPRESSOR may be reduced to be controlled to be equal to or lower than the reference condensing pressure.
However, as the inverter compressor uses a Direct Current (DC) power source as a power source, an actuator for converting an Alternating Current (AC) power source into a DC power source and converting the DC power source into a desired frequency is required. Thus, there is a disadvantage in that the cost increases.
Also, fig. 3 illustrates a state in which a second condenser and a cooling fan are further installed in a heat pump cycle applied to the condensing type laundry dryer.
A second CONDENSER (CONDENSER)26 and a cooling fan 23 are attached to the first CONDENSER 16 of the heat pump cycle 14, and when the temperature of the first CONDENSER 16 rises to a predetermined temperature or higher, the second CONDENSER 26 and the cooling fan 23 cool the first CONDENSER 16 by air outside the dryer, and discharge additional heat inside the cycle.
However, there is a problem in that the cost for installing the second condenser 26 and the cooling fan 23 is increased.
And, fig. 4 is a graph showing a pressure line graph according to an on/off operation time of the constant speed type compressor.
According to the operation control method of the constant-speed compressor shown in fig. 4, when the condensing pressure of the condenser reaches the reference condensing pressure, the compressor is temporarily stopped and then operated again, so that the condensing pressure can be controlled to be maintained at a pressure lower than the reference condensing pressure.
However, according to the operation control method of the constant speed type compressor, since the operation stop and the re-operation are repeated, the drying time is extended, thereby wasting energy for driving the circulation fan and the drum.
Disclosure of Invention
Accordingly, an object of the present invention is to provide a condensing type laundry dryer and a control method thereof, which can solve the problem of a seamless structure between a circulation duct and a heat exchanger by reducing an increased evaporation pressure and a condensation pressure to a pressure level lower than a desired pressure level as drying is performed in the condensing type laundry dryer to which a heat pump cycle is applied.
In order to achieve an object of the present invention as set forth above, a condensing type laundry dryer of the present invention may include: a drum for accommodating the dried object; a circulation duct forming a circulation flow path for circulating air through the drum; a circulation fan for circulating air along the circulation duct; a heat pump cycle including an evaporator and a condenser that are disposed in the circulation duct in a spaced manner, the heat pump cycle causing the evaporator to absorb heat of air discharged from the drum by using a working fluid that circulates through the evaporator and the condenser, and causing the condenser to transfer the heat to air flowing into the drum; a bypass flow path formed in the circulation duct, for bypassing a part of air discharged from the drum around the evaporator, and merging the air passing through the evaporator on an upstream side of the condenser; and an opening/closing means provided in the bypass flow path for selectively opening/closing the bypass flow path.
According to an example of the present invention, the bypass passage may be formed inside the circulation duct.
According to an example of the present invention, the bypass passage may be formed at an upper portion of the evaporator.
According to an example of the present invention, in the bypass flow path, a part of the circulation duct in which the evaporator is located is expanded so as to be wider than a cross-sectional area of the evaporator with respect to a direction intersecting a moving direction of the air, and is narrowed again at an inlet of the condenser.
According to an example of the present invention, the opening and closing unit may include: a damper coupled to the bypass flow path in a hinged manner, for opening and closing the bypass flow path; and an actuator for driving the damper to be rotatable.
According to an example of the present invention, the actuator may be constituted by a solenoid, and the solenoid may include: a housing having a coil built therein; and a plunger connected to a rear surface of the damper and movably provided in the housing, wherein the plunger operates to maintain a state of closing the damper when the coil is powered on, and the damper is opened by an air flow when the coil is powered off.
According to an example of the present invention, the heat pump cycle may include: a circulation pipe forming a circulation flow path for rotating the working fluid through the evaporator and the condenser; a compressor provided in the circulation pipe, for compressing the working fluid discharged from the evaporator to transfer the working fluid to the condenser; and an expansion unit provided in the circulation pipe, for reducing a pressure of the working fluid discharged from the condenser to transfer the working fluid to the evaporator.
In order to achieve an object of the present invention, a control method of a condensing type laundry dryer of the present invention controls the condensing type laundry dryer, the condensing type laundry dryer including: a circulation duct forming a circulation flow path so that air is circulated through the drum; an evaporator and a condenser which are arranged in the circulation duct so as to be spaced from each other, and through which the air passes; and a heat pump cycle for allowing the evaporator to absorb heat of air discharged from the drum by using a working fluid circulated through the evaporator and the condenser, and transferring the heat to air flowing into the drum by using the condenser, wherein the method for controlling the condensing type laundry dryer may include: detecting at least one of an evaporation pressure of the evaporator and a condensation pressure of the condenser; and comparing the detected pressure value with a reference pressure value to distribute the air inside the circulation duct to the bypass flow path and the evaporator so that the air discharged from the drum passes through the evaporator and the condenser, or so that at least a part of the air discharged from the drum bypasses the evaporator through a bypass flow path formed in the circulation duct and joins the air passing through the evaporator on the upstream side of the condenser.
According to an example of the control method of the present invention, the step of distributing air may include a step of adjusting an opening degree of the bypass flow path as the evaporation pressure and the condensation pressure increase.
According to an example of the control method of the present invention, in the step of distributing air, when at least one of the evaporation pressure and the condensation pressure is equal to or greater than a reference pressure value, the degree of opening of the bypass flow path may be increased.
According to an example of the control method of the present invention, the degree of opening of the bypass passage may be adjusted by a damper provided rotatably to open and close the bypass passage and an actuator for driving the damper.
According to the present invention configured as above, the evaporation pressure of the evaporator can be reduced by bypassing a part of the wet steam at the inlet of the (BYPASS) evaporator. Further, the air passing through the evaporator needs to pass through the bypass flow path having a relatively small flow path resistance, and the flow path resistance on the entire air side needs to be reduced, thereby obtaining an effect of increasing the air volume.
Thus, the mass flow rate of air passing through the condenser can be increased to improve the heat radiation performance.
By using the composite effect, the condensing pressure can be maintained below the reference pressure, and the circulating continuous operation can be carried out, thereby helping to shorten the drying time and save energy.
Furthermore, the cost can be saved by preventing the evaporation pressure and the condensation pressure from rising without using an inverter compressor or additionally installing a second condenser.
Drawings
Fig. 1 is a schematic diagram showing an example of a condensing type laundry dryer to which a heat pump cycle is applied.
Fig. 2 is a diagram illustrating the flow of air through an evaporator and a condenser in a condensing laundry dryer to which a heat pump cycle is applied.
Fig. 3 illustrates a state in which a second condenser and a cooling fan are further installed in a heat pump cycle suitable for the condensing type laundry dryer.
Fig. 4 is a graph showing a pressure line graph according to an on/off operation time of the constant speed type compressor.
Fig. 5 is a schematic view of a condensing type laundry dryer of the present invention.
Fig. 6 shows a state in which the bypass flow path is closed in the circulation duct of the present invention.
Fig. 7 shows a state in which the bypass flow path of fig. 6 is opened.
Fig. 8 is a schematic diagram showing the structure of the bypass flow path opening/closing means of the present invention.
Fig. 9 is a graph showing changes in enthalpy of Pressure (PH) diagrams in the case of no bypass flow path and the case of a flow path.
Fig. 10 is a flowchart illustrating a control method of a condensing type laundry dryer of the present invention.
Detailed Description
Hereinafter, a condensing type laundry dryer having a heat pump and a control method thereof according to the present invention will be described in more detail with reference to the accompanying drawings. In this specification, the same or similar structures are given the same or similar reference numerals even in embodiments different from each other, and the description thereof is replaced with the initial description. As used in this specification, the singular expressions include plural expressions as long as other different meanings are not explicitly referred to in the context.
The present invention relates to a condensing type clothes dryer and a control method thereof, which can control the evaporation pressure and the condensation pressure rising along with drying below a predetermined pressure.
Fig. 5 is a schematic view of a condensing laundry dryer with a heat pump cycle 140 according to the present invention.
The condensing type laundry dryer includes a drum 110 for receiving the laundry to be dried.
The casing forms the outer shape of the drier, and has circular opening in the front for throwing in the dried matter, and door hinged to the front side of the casing to open and close the opening.
The control panel is provided at an upper front end of the cabinet so that a user can easily operate the control panel, and the control panel may be provided with an input part for inputting various functions of the dryer, etc., and a display part for displaying an operation state, etc. at the time of drying.
The drum 110 may have a cylindrical shape. The drum 110 may be rotatably disposed in a state of lying horizontally inside the housing. The drum 110 may be driven using a rotational force of a driving motor as a power source. A belt (not shown) is wound around the outer circumferential surface of the drum 110, and a part of the belt is connected to an output shaft of the drive motor. Thus, when the driving motor is operated, power is transmitted to the drum 110 by the belt, and the drum 110 is rotated.
A plurality of lifters are provided inside the drum 110, and when the drum 110 rotates, the laundry such as wet laundry (also referred to as "cloth") that has finished being washed rotates along the drum 110 by the lifters, and repeats an operation (also referred to as "TUMBLING") of dropping into the drum 110 by gravity at the vertex of the rotation trajectory, thereby drying the laundry inside the drum 110, and thus, drying time can be shortened and drying efficiency can be improved.
The condensing type laundry dryer includes a circulation duct 120, and the circulation duct 120 forms a circulation flow path such that air circulates through the drum 110.
The circulation duct 120 may be constituted by first to third ducts. The first duct connects an outlet of the condenser 142 and a rear side of the drum 110 (an inlet of the drum 110 if the air moving direction is taken as a reference) so that the air discharged from the condenser 142 flows into the inside of the drum 110. The second duct connects the front side of the drum 110 (the outlet of the drum 110) and the inlet of the evaporator 141 so that the air discharged from the drum 110 can flow into the inlet of the evaporator 141. The third pipe connects the outlet of the evaporator 141 and the inlet of the condenser 142 such that the air discharged from the evaporator 141 flows into the inlet of the condenser 142. As described above, the air may circulate the condenser 142, the drum 110, and the evaporator 141 through the circulation duct 120 configured of the first to third ducts.
The condensing type laundry dryer may include a circulation fan 130, and the circulation fan 130 may be configured to flow air such that the air circulates along the circulation duct 120.
The circulation fan 130 may be connected to a driving motor to be driven. In this case, a belt is connected to one side of an output shaft of the driving motor, and a circulation fan 130 may be connected to the other side of the output shaft.
The condensing laundry dryer may have a heat pump cycle 140.
The heat pump cycle 140 absorbs heat from a low-temperature heat source such as air discharged from the outlet of the drum 110, stores a high-temperature heat source in a working fluid (refrigerant), and discharges heat using air flowing into the inlet of the drum 110. Thereby, heat discarded by the air discharged from the drum 110 is recovered and used to heat the air flowing into the drum 110.
The heat pump cycle 140 may be composed of an evaporator 141, a condenser 142, a compressor 143, and an expansion unit 144. The heat pump cycle 140 has a circulation line through which a refrigerant as a working fluid circulates. The circulation pipe is formed separately from the circulation pipe 120, and the evaporator 141, the compressor 143, the condenser 142, and the expansion unit 144 are connected by the circulation pipe such that the refrigerant circulates through the evaporator 141, the compressor 143, the condenser 142, and the expansion unit 144. Wherein the circulation pipe 120 and the circulation pipe commonly pass through the evaporator 141 and the condenser 142. That is, the air of the circulation duct 120 and the refrigerant of the circulation duct commonly pass through the evaporator 141. In the evaporator 141, the air and the refrigerant can thereby exchange heat with each other.
The evaporator 141 may be a fin & tube type heat exchanger configured of a heat transfer pipe having a plurality of heat transfer plates and a refrigerant flow path. The heat transfer plates are arranged at a distance from each other in a direction intersecting the air moving direction and are arranged perpendicularly to each other, so that air can pass through the air flow path formed between the heat transfer plates when passing through the evaporator. The heat transfer tube has a refrigerant flow path for allowing a refrigerant to flow inside the heat transfer tube. The heat transfer tubes may be joined to the heat transfer plate so as to penetrate therethrough, and the heat transfer tubes may be arranged to be spaced apart in the vertical direction. The heat transfer pipes arranged at intervals may be connected to each other by a connection pipe bent in a semicircular shape. The heat transfer pipe connected in this way penetrates a plurality of heat transfer plates many times, and the contact area with the heat transfer plates and air can be expanded. The heat transfer plates expand the heat transfer area between the refrigerant and the air in the heat transfer tubes, and contact the heat transfer tubes, thereby exchanging the heat transferred from the heat transfer tubes with the heat of the air. When passing through the evaporator 141, the air flows into the air inlet of the evaporator 141, moves along the air flow path, and flows out of the air outlet of the evaporator 141. When passing through the evaporator 141, the refrigerant flows into the inlet of the refrigerant flow path, moves along the refrigerant flow path, and flows out of the outlet of the refrigerant flow path. The air flow paths between the heat transfer plates can be separated from the refrigerant flow paths by the heat transfer tubes, so that the air can be mutually transferred without being mixed with the refrigerant.
The condenser 142 may be constructed in the same manner as the evaporator 141. The evaporator 141 and the condenser 142 are different from each other in function, and are heat exchangers that perform heat transfer and heat exchange between air and refrigerant. The evaporator 141 or the condenser 142 may be a plate-shaped heat exchanger in which a first heat transfer plate having an air flow path and a second heat transfer plate having a refrigerant flow path are alternately laminated and joined to each other.
In the condensing type laundry dryer, the temperature of the air discharged from the outlet of the drum 110 is relatively lower than the temperature of the air flowing in from the inlet of the drum 110, but it is sufficient in that the evaporator 141 absorbs the heat of the air discharged from the outlet of the drum 110.
The evaporator 141 is provided inside the circulation duct 120. And, the evaporator 141 is connected to the outlet side of the drum 110 through the circulation duct 120 (second duct), so that heat can be absorbed from the air at the outlet of the drum 110. That is, in the evaporator 141, heat of air is transferred to the refrigerant. Accordingly, the air at the outlet of the drum 110 is snatched out of heat by the evaporator 141, and is cooled and discharged from the outlet of the evaporator 141. At this time, since the air discharged from the outlet of the drum 110 is in a humid state, the evaporator 141 may perform a dehumidifying function as cooling the air at the outlet of the drum 110. In contrast, the refrigerant absorbs heat in the evaporator 141, and is thus heated and discharged from an outlet of the evaporator 141.
The condenser 142 is disposed inside the circulation duct 120. The condenser 142 may be disposed inside the circulation duct 120 so as to be spaced apart from the evaporator 141. The condenser 142 is connected to an outlet of the evaporator 141 by means of a circulation duct 120 (third duct), so that air discharged from the evaporator 141 flows into an inlet of the condenser 142. The refrigerant passing through the condenser 142 receives heat from the air at the outlet of the drum 110, thereby transferring heat to the air in the condenser 142. Accordingly, the air introduced into the condenser 142 may be heated in the condenser 142, discharged from the outlet of the condenser 142, and introduced into the inlet of the drum 110. Instead, the refrigerant discharges heat in the condenser 142, condenses in a liquid state, and is discharged from an outlet of the condenser 142. The refrigerant is changed into a high-temperature and high-pressure liquid in the high-temperature and high-pressure gas and is phase-changed, so that the latent heat of condensation of the refrigerant generated at this time is discharged to the air flowing into the drum 110, and the discharged heat is used to heat the air flowing into the drum 110.
As described above, in order to move heat from the evaporator 141, which is a low temperature portion receiving heat, to the condenser 142, which is a high temperature portion discharging heat, driving energy is required. In the present invention, electric energy may be used as the driving energy. The electric energy is used to drive the compressor 143, and the compressor 143 is used to compress a refrigerant that is a working fluid of a heat pump cycle. Driving using thermal energy may be used in addition to electric energy. An absorption heat pump using steam, high-temperature water, gas, or the like is a representative example. And. The heat pump can be operated by an engine that burns a gas, in a manner of obtaining power by an engine that directly burns a fuel, or driving the compressor 143 that compresses a refrigerant. Further, power can be obtained from a stirling engine that uses an engine driven by a heat source.
The heat pump system described above has the greatest advantage that energy of a larger amount than required for driving can be supplied in the form of thermal energy, and thus energy efficiency can be increased.
The vapor compression heat pump cycle 140 driven by electric energy includes a compressor 143, a condenser 142, an expansion unit 144, and an evaporator 141.
The compressor 143 may be connected to the evaporator 141 and the condenser 142 by circulation pipes, respectively.
The circulation pipe may be constituted by the first to fourth pipes. The first pipe connects the evaporator 141 and the compressor 143 such that the low-temperature, low-pressure gas-phase refrigerant evaporated from the evaporator 141 is discharged from an outlet of the evaporator 141.
The compressor 143 compresses a low-temperature and low-pressure gas-phase refrigerant to change the refrigerant into a high-pressure gas having a temperature higher than that of the air discharged from the drum 110, and can discharge heat to the air flowing into the drum 110 among the high-temperature and high-pressure refrigerants. The discharge of this heat is performed in the condenser 142, and the refrigerant is cooled to become liquid in a high-pressure state. When the pressure is reduced by the expansion unit 144 such as an expansion valve or a capillary tube, the temperature of the refrigerant is rapidly reduced, and the refrigerant becomes a low-temperature, low-pressure saturated refrigerant. Since the refrigerant in a low temperature state can absorb heat from the outside, the refrigerant becomes a low-temperature and low-pressure gas when the evaporator 141 absorbs heat from the air at the outlet of the drum 110, and finally, the heat pump cycle 140 in which the heat absorbed by the evaporator 141 is discharged by the condenser 142 is realized when the gas is sent to the compressor 143 again.
The condensing laundry dryer of the present invention includes a bypass flow path 150 for controlling an evaporation pressure and a condensation pressure below a predetermined pressure together using basic characteristics of the heat pump cycle 140.
Fig. 6 shows a state in which the bypass flow path 150 is closed in the circulation duct 120 of the present invention, and fig. 7 shows a state in which the bypass flow path 150 of fig. 6 is opened. Fig. 8 is a schematic diagram showing the configuration of the bypass flow path 150 opening/closing means of the present invention, and fig. 9 is a graph showing changes in pressure enthalpy diagrams in the case where there is no bypass flow path 150 and in the case where there is a bypass flow path.
A bypass flow path 150 is formed in the circulation duct 120 so that a part of the air discharged from the drum 110 bypasses the evaporator 141 and joins the air passing through the evaporator 141 at an upstream side of the condenser 142.
The air discharged from the outlet of the drum 110 flows into the inlet of the drum 110 again through the evaporator 141 and the condenser 142, and the upstream side of the condenser 142 is located between the evaporator 141 and the condenser 142 in the circulation duct 120.
The bypass flow path 150 may be a portion of the circulation duct 120.
The bypass flow path 150 may be formed inside or outside the circulation duct 120.
The bypass flow path 150 shown in fig. 6 is formed inside the circulation duct 120.
In the bypass flow path 150, a part of the circulation duct 120 in which the evaporator 141 is located is expanded to be wider than the cross-sectional area of the evaporator 141 with reference to the direction intersecting the moving direction of the air, and is narrowed again at the inlet of the condenser 142.
In order to form the bypass flow path 150 inside the circulation duct 120, the sectional area (the direction crossing the air flow direction, more precisely, the direction perpendicular to the air flow direction) of the circulation duct 120 where the evaporator 141 is located is made wider than the size (or the sectional area) of the evaporator 141, so that a GAP (GAP) may be formed between the circulation duct 120 and the evaporator 141. For example, the diameter (in the case where the cross-sectional shape of the circulation duct 120 is a quadrangle, the lateral direction or the height) of a part of the circulation duct 120 (the part where the evaporator 141 is provided) may be formed by an expanded shape. In the case where the sectional area of the circulation duct 120 is formed in a quadrangle shape, the height is higher than the evaporator 141 so that the evaporator 141 is in contact with the bottom surface of the circulation duct 120 and a gap may be formed above the evaporator 141. Accordingly, the bypass flow path 150 is formed above the evaporator 141 with reference to the gravity direction, and when the bypass flow path 150 is opened, a part of the air can bypass the evaporator 141. At this time, when the temperature of the air discharged from the drum 110 is, for example, about 40 ℃, since the density of the air is low and the air becomes light and rises inside the circulation duct 120, it is preferable that the bypass flow path 150 is formed at the upper portion of the evaporator 141.
Further, the size of the cross-sectional area of a portion of the expanded circulation duct 120, that is, the bypass flow path 150, becomes smaller toward the downstream side of the evaporator 141, so that the air bypassing the evaporator 141 can be merged with the air passing through the evaporator 141.
The bypass flow path 150 shown in fig. 6 is formed above the evaporator 141, but can be realized in various forms as follows. For example, the bypass flow path 150 may be formed at a lower portion of the evaporator 141, or may be formed at both upper and lower portions of the evaporator 141. Also, a bypass flow path 150 may be formed between a side surface of the evaporator 141 and the circulation duct 120. The bypass flow path 150 may be formed to penetrate the evaporator 141.
The bypass flow path 150 shown in fig. 5 may branch from the circulation duct 120, extend along the outside of the circulation duct 120, and merge again into the circulation duct 120.
For example, the bypass flow paths 150 may branch from the upstream side of the evaporator 141 of the circulation duct 120 and merge at the downstream side of the evaporator 141, so that the air bypasses the evaporator 141 and joins in the condenser 142. At this time, one side of the bypass flow path 150 communicates with the upstream side of the evaporator 141, and the other side of the bypass flow path 150 communicates between the downstream side of the evaporator 141 and the upstream side of the condenser 142. The upstream side of the evaporator 141 may be an inlet side of the evaporator 141, and the downstream side of the evaporator 141 may be an outlet side of the evaporator 141.
The condensing laundry dryer includes an opening and closing unit for selectively opening and closing the bypass flow path 150.
The opening and closing unit may include a damper 151, the damper 151 being hinge-coupled with the bypass flow path 150, and an actuator for driving the damper 151.
The damper 151 may have a plate shape with a predetermined size. One end of the damper 151 is coupled to the bypass flow path 150 by a hinge, and the other end of the damper 151 is capable of opening and closing the bypass flow path 150 by rotation. Further, since the elastic sealing member 152 is provided at the other end portion of the damper 151, the sealing member 152 prevents air from flowing into the bypass flow path 150 when the damper 151 is closed.
The actuator may be a solenoid 160 or a solenoid valve. The solenoid 160 may be comprised of a housing 161, a coil 162, and a plunger 163.
The coil 162 is provided inside the case 161, and when power is applied to the coil 162, a magnetic path surrounding the coil 162 is magnetized, and the magnetic field of the magnetic path generates a magnetic force in the plunger 163, thereby instantaneously moving the plunger 163.
A connection portion 151a for connection with the solenoid 160 may be formed on the rear surface of the damper 151. The plunger 163 of the solenoid 160 is coupled to the connection portion 151a in a hinged manner, so that the rotational operation of the damper 151 can be smoothly performed as the power generated in the solenoid 160 is transmitted to the damper 151.
The actuator may be constituted by a motor or a cylinder mechanism in addition to the solenoid 160.
When the damper 151 is opened and closed by the motor and the cylinder mechanism, the opening angle of the damper 151 can be precisely controlled.
The damper 151 shown in fig. 6 is operated by a solenoid 160.
When the bypass flow path 150 is to be closed, as shown in fig. 6, the solenoid 160 provided in the bypass flow path 150 is Opened (ON), and the bypass flow path 150 above the evaporator 141 is closed. In this case, the air discharged from the drum 110 passes through the evaporator 141 and the condenser 142 in order. At this time, the air flow rate through the evaporator 141 and the air flow rate through the condenser 142 are the same.
When the bypass flow path 150 is to be opened, as shown in fig. 7, when the solenoid 160 is closed (OFF), the flow of air naturally pushes up the damper 151 in the opening direction. In this case, a part of the air discharged from the drum 110 flows into the bypass passage 150 having a small passage resistance, and the rest of the air passes through the evaporator 141. At this time, the air flow rate through the evaporator 141 may be smaller than the air flow rate through the condenser 142. This is because the air moving along the bypass flow path 150 bypasses the evaporator 141 and merges at the upstream side of the condenser 142, and thus the sum of the air flow rate flowing along the bypass flow path 150 and the air flow rate passing through the evaporator 141 is the same as the air flow rate passing through the condenser 142.
As described above, as the damper 151 is opened, a part of the wet steam Bypasses (BYPASS) the inlet of the evaporator 141, so that the heat obtained from the evaporator 141 can be reduced to lower the evaporation pressure. Further, as the air passing through the evaporator 141 is required to pass through the bypass flow path 150 having a relatively small flow path resistance, the flow path resistance on the entire air side is reduced, and the effect of increasing the air volume is obtained. This increases the mass flow rate of air passing through the condenser 142, and thus the heat radiation performance can be improved. According to this composite effect, the condensing pressure can be maintained below the reference pressure as shown in fig. 9. Further, even if the constant speed compressor 143 is used, the continuous operation of the cycle can be performed, and the rapid decrease in the dehumidification efficiency can be prevented in advance.
Fig. 10 is a flowchart illustrating a control method of a condensing type laundry dryer of the present invention.
The method for controlling the condensing type clothes dryer of the present invention is a method for controlling the evaporating pressure of the evaporator 141 below a predetermined pressure by adjusting the opening degree of the bypass flow path 150.
The above-mentioned condensing type laundry dryer includes: a circulation duct 120 forming a circulation flow path so that air circulates through the drum 110; an evaporator 141 and a condenser 142 which are disposed in the circulation duct so as to be spaced apart from each other, and through which the air passes; and a heat pump cycle 140 for allowing the evaporator 141 to absorb heat of air discharged from the drum 110 by using a working fluid circulating through the evaporator 141 and the condenser 142, and for allowing the condenser 142 to transfer the heat to air flowing into the drum 110.
The condensing type laundry dryer may include control factors required in the drying process, such as a temperature sensor and a humidity sensor for detecting temperature and humidity at the inlet and outlet of the drum 110. The condensing type laundry dryer may further include pressure sensors 145a and 145b, and the pressure sensors 145a and 145b may measure an evaporation pressure of the evaporator 141 and a condensation pressure of the condenser 142. The condensing type laundry dryer may further include a temperature sensor for measuring outlet temperatures of the evaporator 141, the condenser 142, and the compressor 143.
In particular, the evaporator 141 and the condenser 142 are provided with pressure sensors 145a and 145b, respectively, so that the evaporation pressure and the condensation pressure can be detected.
The laundry dryer of the present invention includes a control unit which can receive a detection signal from the above-mentioned pressure sensor to control the opening degree of the bypass flow path 150.
When observing the control method of the condensing type laundry dryer, the temperature of the air discharged from the outlet of the drum 110 may gradually increase and the evaporation pressure of the evaporator 141 and the condensation pressure of the condenser 142 may increase as a predetermined time elapses after the dryer is operated (step S120).
The pressure sensors 145a and 145b may detect at least one of the evaporation pressure and the condensation pressure.
Next, the control unit compares the detected pressure with a reference pressure value (step S130). According to the comparison result, if the detected pressure is less than or equal to the reference pressure value, a control signal (on signal) is transmitted to the solenoid 160 to close the damper 151, so that the air discharged from the drum 110 flows into the inlet of the evaporator 141 (step S110).
When the damper 151 is closed, the air discharged from the drum 110 passes through the evaporator 141, and the heat of the air flowing into the air flow path of the evaporator 141 is transferred to the refrigerant flowing into the refrigerant flow path of the evaporator 141. Thereby, the wet steam discharged from the drum 110 is cooled in the evaporator 141 and thus dehumidified. The air cooled in the evaporator 141 is discharged from the air flow path and flows into the condenser 142. At this time, all the air flow discharged from the evaporator 141 flows into the condenser 142. The air flowing into the air flow path of the condenser 142 receives heat from the refrigerant flowing into the refrigerant flow path of the condenser 142, is heated, and then flows into the inlet of the drum 110.
When the detected pressure is higher than the reference pressure value (step S130), the bypass passage is opened (step S140), and the air discharged from the drum 110 is distributed to the bypass passage 150 and the evaporator 141 formed in the circulation duct 120. Accordingly, the air flowing in through the bypass flow path 150 bypasses the evaporator 141, and joins the air passing through the evaporator 141 on the upstream side of the condenser 142.
According to the control method described above, the evaporation pressure can be reduced to a predetermined pressure or less as a part of the wet steam discharged from the drum 110 flows into the bypass passage 150 upstream of the evaporator 141 and bypasses the evaporator 141. Further, since the air flow rate of the bypass flow path 150 having a small flow path resistance is increased more than the air flow rate passing through the evaporator 141, the mass flow rate of the air passing through the condenser 142 is increased to improve the heat radiation performance. Thereby, the condensing pressure can be maintained below the reference pressure.
The condensing type laundry dryer having the heat pump described above is not limited to the structure and method of the above-described various embodiments, which may be selectively combined by all or a portion of the respective embodiments, so that various modifications may be implemented.

Claims (9)

1. A condensing laundry dryer, comprising:
a drum for accommodating the dried object;
a circulation duct forming a circulation flow path for circulating air through the drum;
a circulation fan for circulating air along the circulation duct;
a heat pump cycle including an evaporator and a condenser that are disposed in the circulation duct in a spaced manner, the heat pump cycle causing the evaporator to absorb heat of air discharged from the drum by using a working fluid that circulates through the evaporator and the condenser, and causing the condenser to transfer the heat to air flowing into the drum;
a bypass flow path formed in the circulation duct, for bypassing a part of air discharged from the drum around the evaporator, and merging the air passing through the evaporator on an upstream side of the condenser; and
an opening/closing means provided in the bypass flow path for selectively opening/closing the bypass flow path,
the opening and closing unit includes:
a damper coupled to the bypass flow path in a hinged manner, for opening and closing the bypass flow path; and
an actuator for driving the damper to be rotatable,
one end of the damper is hinged to an upper end of the bypass flow path, and the other end of the damper extends toward an upper end of the evaporator in a rotatable manner,
the other end of the damper is provided with a sealing member having elasticity and formed to protrude so as to be contactable with the upper end portion of the evaporator, so as to prevent air from flowing into the bypass flow path when the damper is closed,
the bypass flow path is formed by a portion of the circulation duct being formed to expand upward from an upper portion of the evaporator so as to be higher than the evaporator, and to be narrowed again at an inlet of the condenser.
2. A condensing laundry dryer as claimed in claim 1, wherein said bypass flow path is formed inside said circulation duct.
3. The condensing laundry dryer according to claim 2, wherein in the bypass flow path, a part of the circulation duct in which the evaporator is located is expanded to be wider than a cross-sectional area of the evaporator with reference to a direction crossing a moving direction of the air, and is narrowed again at an inlet of the condenser.
4. A condensing laundry dryer as claimed in claim 1, wherein said bypass flow path is formed at an upper portion of said evaporator.
5. A condensing laundry dryer according to claim 1,
the above-mentioned actuator is constituted by a solenoid,
the solenoid includes:
a housing having a coil built therein; and
a plunger connected to a rear surface of the damper and movably provided in the housing,
when the coil is powered on, the plunger operates to maintain a state in which the damper is closed, and when the coil is powered off, the damper is opened by air flow.
6. A control method of a condensing laundry dryer according to claim 1, characterized by comprising:
detecting at least one of an evaporation pressure of the evaporator and a condensation pressure of the condenser; and
the detected pressure value is compared with a reference pressure value, and the air in the circulation duct is distributed to the bypass flow path and the evaporator, so that the air discharged from the drum passes through the evaporator and the condenser, or at least a part of the air discharged from the drum bypasses the evaporator through the bypass flow path formed in the circulation duct, and joins the air passing through the evaporator on the upstream side of the condenser.
7. The method as claimed in claim 6, wherein the step of distributing air includes the step of adjusting the opening degree of the bypass flow path as the evaporating pressure and the condensing pressure increase.
8. The method of claim 7, wherein in the step of distributing air, the opening degree of the bypass flow path is increased when at least one of the evaporation pressure and the condensation pressure is greater than or equal to a reference pressure value.
9. The method of claim 7, wherein the opening and closing unit includes an actuator for driving the damper, the opening degree of the bypass flow path is adjusted by the damper, and the damper is rotatably provided to open and close the bypass flow path.
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CN105671902A (en) 2016-06-15
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US10793995B2 (en) 2020-10-06
US10196772B2 (en) 2019-02-05
US20190003108A1 (en) 2019-01-03
US20160160427A1 (en) 2016-06-09
EP3031974A1 (en) 2016-06-15
EP3031974B1 (en) 2017-08-30

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